Machine tool transmission and control



0:11.17, 1939. a c, HOLMES 2,176,737

MACHINE TOOL TRANSMISSION AND CONTROL Ofiginal Filed March I1, 1931 10 Sheets-Sheet l.v

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G. c. HOLMES MACHINE TOOL TRANSMISSION AND CONTROL Oct. 17, 1939.

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MACHINE TOOL TRANSMISSION AND CONTROL Ori ginal Filed March 11/1937 10 Sheets-Sheet 3 IN V EN TOR.

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MACHINE TOOL TRANSMISSIONAND CONTROL Original Filed March 11. 1937 10 Sheets-Sheet 4 INVENTOR.

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MACHINE TOOL TRANSMISSION AND CONTROL Original Filed March 11, 1957 10 Sheets-Sheet 5 IN VEN TOR.

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- 7 MACHINE TOOL TRANSMISSION AND CONTROL Original Filed March 11, 1937 10 Sheets-Sheet 1O I zmcm 'QBY 9 v 'ATTORNEY' engagement of sliding gears or clutches of a Patented 0a. 11, 1939 PATENT OFFICE moms TOOL 'rnansmssron AND N'rno Glenn 0. Holmes, Madison, Wis, assignor tcGisholt Machine Company, Madison, Wis., a cor- D ration of Wisconsin Application March 11, 1937, Serial No. 130,273

Renewed February 23, 1939 13 Claims. This invention relates to transmission and control mechanism for machine tools, etc., and more particularly for the spindle transmission of a lathe.

A primary purpose of the invention is to provide an improved transmission clutch device and improved control mechanism therefor, and in a form particularly adapted for machine tool clutches and reversers.

A further purpose of the invention is to provide an improved mechanism, for a mechanical transmission having alternative driving or interrupting means, which will effect a period of less than full driving capacity of the driving-interrupting means during engagement thereof, as for instance to avoid shock upon starting or reversing a spindle transmission in a machine tool, or to assist the spindle transmission.

I A further purpose is to provide a clutch and operatingmechanism therefor particularly adapted for an improved interlocking or interrelated operation of shifting devices for controlling transmission effects of various sorts, as for instance rate change, interruption, reversal and braking.

A further purposeis generally to simplify and improve the construction, operation and relationship of transmission and control mechanism of a machine tool, particularly when the transmission includes reverser or interrupter devices, and

still other objects will be apparent from this specification.

The invention consists in the construction and arrahgement oi' parts as herein illustrated, de-

scribed and claimed, and in such modifications thereof as are equivalent to the structure claimed.

Throughout the specification the same reference characters have been used to'indicate the same parts, and in the drawings:

Figure l shows a front view of a headstock'and spindle drive portion of a lathe in which the invention= is incorporated;

Figure 2 is a left end elevation of the same structure. v

Figure 3 is a vertical section, taken approximately along the line 3-3 of Fig. l'and enlarged.

Figure 4 is a sectional development of the transmission for the spindle of the lathe shown in Fig. 1, taken approximately along the line Figure 8 is a vertical section of the same controller unit and associated structure, taken approximately along line 8-8 of Fig. '7.

Figures 9, 10, 11, 12, 13,14 are vertical sections 'of the same controller unit, taken respectively along lines 99, |0 l0, "-4 I, l2-l2, l3-l3 and ll-ll of Fig. '7. v

Figure 15 is a more or less diagrammatic view showing certain control mechanism of the machine and certain interconnections thereof.

Figure 16 is a perspective view of a speed change controller. i

Figures 17, 18 are partial sections showing respectively top and side views of a pressure delay device associated with the rate change piston devices.

Figure 19 is a. vertical section of a control device associated with the spindle reverser.-

Figure 20 is an enlarged section, in somewhat greater detail, of the primary shaft of the transmission shown in Fig. 4, and mechanism associated therewith.

Figure 21 is a transverse section taken along line 2|, 2| of Fig. 20.

The machine of the drawings .is a lathe, of the same construction as that shown in said copending application, Serial No. 83,306, which includes a bed, a portion of which is shown at I, Fig; 1, upon which a headstock, generally denoted by the numeral 2, is mounted. A spindle 3, Figs.

1, 4, is driven from a power source associated with 5 the machine, in this case a drive pulley 4. The

lathe has suitable tool supports, not shown, driven through a feed train which may be any of several well known types drivenv from the spindle 3 :through a feed gear such as 5, Fig. 4. Spindle transmission mechanism is provided for driving spindle-3 from pulley 4 at a variety of rotational speeds, the transmission being of improved form and arrangement as more particularly pointed out in a co-pending application of Werner Irving Senger, Serial No. 117,305, filed December 23, 1936. The spindle transmission includes the pul-l ley 4, a reverser-interrupter generally denoted by the numeral 3, Fig. 4, and a rate'change device generally denoted by the numeral 1, the pulley, reverser, rate changer and-certain other mechanism being unitarily carried by a removable housingmember 8, Figs. 2, 4, which is rigidly fixed with an upstanding housing portion 8 car-' ried by bed i, in which spindle 3 is rotatably mounted, as more particularly described in said copending application Serial 1101117305.

The reverser-interrupter 5 is of the following construction: Pulley 4, Fig. 4, is fixed on a shaft i8, Figs. 4, 20, 21 which carries a plurality of outer clutch members ii, i2 each independently rotatable and respectively keyed with the alternate driven plates ofdifferent friction plate groups i3, i4 of different driving clutches each having alternate driving plates keyed to an inner member i5 which is slidabiykeyed on shaft l8. The member ii drives a shaft i3'through meshed gears i1, i8. Member i2 drives shaft i 3 through double sprockets i3, 28, the sprockets being connected by drive chains such as 2|, Fig. 3. The inner member i5 provides an annular abutment portion 22, and is axially shiftable to alternatively cause frictional engagement between the plates of group i3, or oppositely to cause engagement of the plates of group i4, and the arrangement is such that as member i5 is shifted in opposite directions the shaft i3 is driven in forward and reverse directions.

The spindle rate changer .1 is constructed as follows: A shaft 23, Fig. 4, is driven from shaft i3 through a rate change device which includes the gears 24, 25, 23 fixed together and slidably keyed on shaft i3 and respectively engageab'le one at a time with gears 21, 28, 23 which are fixed on shaft 23. A shaft 33 is driven from shaft 23 through a rat: change device .which' includes the gears, 32, 33 fixed together and slidably keyed on shaft 38 and respectively engageable one at a time with a gear 34, the gear 28 and another gear 5 35, each of the gears 34 and" being also fixed on shaft 28. A gear 33 is fixed on a sleeve 3311 which is rotatably supported on the extended end 38a of shaft '38, sleeve 33a and gear 33 Being driven from shaft 38 through a rate change device which includes a clutch gear 31 shiftable toengage internal clutch elements 33b on sleeve 33a, in which case gear 83 is driven at the same speed as the shaft 38, or to engage gear 83 of a reduction train consisting of gear 38, a shaft 38 co-axial with the shaft 23, and a gear 43 which meshes with gear 33, in which case gear. 33 is driven at relatively slow speed. The gear 33 drives spindle 3 and feed gear 5 through a meshed gear 4| fixed on the spindle, and the several rate change devices and the reverser provide for eighteen changes of rotational spindle speed. substantially in a geometrical progression, and in either direction.

A spindle brake device generally denoted by the numeral 42, Fig. 6, includes a brake drum of friction wheel 43, Figs. 4, 6, a friction band 43a anchored at the one end with a stud 44 and normally urged toward released position by a spring 45 acting on an abutment member 43 which is fixed to the band.

The reverser 3, the various rate change units, andbrake 42 are provided with means for this power operation including fiuid operable piston devices as follows:

A reverser piston device for reverser 3, generally denoted by the numeral 41, Figs. 4, 15, 28,

includes a fluid operable piston 48, a cylinder 43, and a piston rod 58 provided with a coupling unit 5i which couples the piston to the adjacent end 52 of a shifter rod 53 slidable in an axial bore of the shaft i8, and rotatable with the shaft, rod 53 being extended to carry a shifter member 54, Figs. 4, 20, 21 which extends radially outwardly through suitable slots in the shaft i8 to-engage at its ends with the slidably keyed reverser clutch member l5, whereby, as piston 48 is shifted, the abutment portion 22 of the member i5 is correspondingly shifted to operate the reverser 3. The coupling unit 5i includes an anti-friction thrust bearing 5ia having its inner race fixed on rod 58 as by a nut 53!! and suitable thrust members 5"), Bic fixed on piston rod 58 and engaging theouter racefithere being suitable means, as rod 5id preventing rotation of the thrust members and piston rod.

The piston 48 of reverser piston device 41 may be alternativelyoperated in the one or the other direction, wherebyto engage the reverser 3 for forward or reverse rotation, by fiuid pressure from suitable ports 53, 51, Fig. 4. Fluid pressure is continuously supplied to piston device 41 from a port 58 which continuously tends to shift reverser 5 to its central or non-engaged position, the pressure from port 58 acting at the one end of the device against an extended portion 58 of piston rod 58, and at the other end of the device against a shouldered sleeve 38. Whenever fiuid pressure is applied through either port 53, 51 the piston 48 and rod i8 are shifted against the resistance of the fluid pressure from port 58 by reason of the relatively large area of piston 48, but when pressure is released from both ports 53, 51 the piston device 41 and reverser 3 will immediately be shifted to central non-driving position, the fluid from port 58 then simultaneously forcing the sleeve 38 to the right against a shouldered portion 380. and forcing the piston rod to the left until the piston rests against the end of sleeve 38.

A spindlebrake piston device, generally denoted by the'numeral 31, Figs. '7, 15, includes a piston 3lu, having a rod 62, Figs. 8, 7. Piston 3la may be forced to the left in Fig. 7, as will be later explained, to overcome spring 45 and engage brake 42, or may be forced in the other direction to permit spring 45 to release the brake. For the speed change device comprising the shiftable gears 24, 25, 23, Figs. 4, 15, 'there is provided a shifter including a piston device generally denoted by the numeral 33, Figs. 8, 15, which includes a piston 33a, upon the piston rod 33b of which is fixed a shifter arm 33c engaging a suitable annular groove. in the gear unit.

For the speed change device comprising the shiftable gears ll, 32, 33, Figs. 4, 15, there is which includes a piston\ 35a upon the piston rod m of which is fixed shifter arm m engaging a suitable annular groove in the hub of the gear.

For the operation of the several piston devices a pressure fiuid source, such as a pump of any suitable'type, as indicated at 33,1"ig. 15, is driven whenev pulleyv 4 is running. as for instance a on the exposed peripheries of flange members shown in Fig. 15 which may, for instance, be

- formed by the lower portion of the spindle gear 'pismn devices is provided as follows:'* v

A speed selector device, generally indicated by the numeral 1|, Figs. 3,-.1'6 is similar to that shown in said copending application, Serial No. 58,549, which will therefore be here only briefly described. The selector device includes a fixed indicator pointer 12 against which a plurality of charts ,or scales are readable. One of the charts includes numerals such as 13 arranged 14, 15 which are both fixed for'rotation with a shaft 16. The numerals 18 are arranged inconsecutive order and correspond with the'rotative speeds available for spindle 3 upon operation of the several rate change-devices to their various position combinations. Another chart readable against indicator 12 includes numerals such as 11 arranged on the periphery of an annular member 18 which is frictionally held to be normally rotatable with the flange members l4, 18, but is adjustable relative thereto by the means of a handle 19 which projects through a slot 88 in the member 15. The numerals 1'! indicate diflerent work diameters within the speed range 'of the. machine'and arranged in consecutive order.

Still another chart includes numerals such as I 81, arranged in consecutive order on the face of the member 18 to be visible through slot 88 and readable againstan indicator pointer or arrow 82 which is rotatable with shaft 18. The numerals of .the last mentioned chart are arranged to indicate surface or peripheral speed on the work piece rotating with the spindle.

As illustrative of the use of the speed selector device there is selected on the chart 8| a desired peripheral speed suitable for the turning tool used and for the work material to be operated upon, the member 18 being turned by lever I9 until that peripheral speed is indicated against the pointer 82. Shaft' 18 is then turned in either direction by the means'of handles such as 83 until the diameter of the work piece as listed on the chart 1! is indicated'against the pointer 12. If ,thisdoes not exactly correspond to an available rotational speed, as indicated on chart l3 then choice must be made of a slightly higher or lower rotational speed, the rotatlve speed thus selected being aligned with pointer 12-, whereupon the shifter devices, later described, will shift the ratechange devices to effect the desired speed.

. The positioning of theselector device, as described eifects the selected speed by the means jofimechanism as follows:-

umShaft 16, F g. 3, is. coupled for rotation with a coaxial shaft 84 Figs. '7, 8 by the means of an .zaxially djsengageable tongue and slot coupling inolicatedv at 85, Fig. 8. Fixed on'shaft 84 are Eva-plurality of cam members 86,81, 88, 89, 98,

9] 92 98, Figs. 8, 15 separated by spacers such by a gear 10, Fig. 4, fixed on shaft in, the pump drawing oil from a sump 89a, diagrammatically as 94, 95, to operate various pop t valves which control the shifting of the piston devices to eifect rate changing.

Thus, for controlling the movement of the piston device 83 the cams 81, 88, 89, Figs. 8, 15 respectively operate 'thepoppet valves 81a, 88a, 89a. For'piston device 84 the cams 98, 9|, 92 operate poppet valves 98a, 9|a, 92a and for piston device the cam' 98 operates both the poppet valves 98a, 98a. In each instance the configuration of the cams is such that as shaft 84 is rotated one only of the poppet valves of each piston device is opened by the cams in each angular position of the shaft 84 corresponding to the, points where the difierent rotative speed indicating chart numerals 19 read against the indicator pointer 12. In each such positions the cams are cut away to permit the fluid pressure to close the other valves of the set against their seats. It will be understood that in the drawings the cams. are more or less diagrammatically shown, but it will be obvious that in each device the cams may be formed to operate as just described.

The different poppet valves of the piston devices 88, 84, 85 each communicate with a different port-of the associated piston device, the ports being spaced in the direction of piston movement according to the diiferent piston positions re- .quired. .Opening the poppet valve results in movement of the piston of the device to. a position corresponding'to the port leading to the open valve, whereby to shift the speed change units to the indicated speed position. As illustrative of this action the operation of the piston device 64 is as follows:

Referring to Figs. 9, 10, the piston device 64 has ports 98b, 9"), 9217 respectively controlled by poppet valves 98a, 9la, 92a through suitable channels. In each instance opening the poppet valve will provide afluid drain for the port. The ports are spaced in accordance with the three positions required for. the piston 64a. Fluid is supplied to the piston device through a channel groove 91b and a valve member 98 which may move axially in either direction. In the one direction of movement valve 98 seats against a member 99 to prevent flow of fluid from channel 91b to a groove it!!! which communicates directly with port 9), and with the poppet valve 9la through a channel We. In the other direction of movement valve 98 seats against a member llll to prevent flow of fluid to the port 92b and to poppet valve 92a through the channels lilla, llllb. Thus if either poppet valve 9la'or 92a is opened the resulting reduction of pressure movesvalve 98 in the direction of the opened poppet valve, and holds it in' position closing the flow of fluid fromgsupply channel 91b to the open valve. This leaves the one end of piston 64a connected to the pressure supply. and the other connected to the open poppet valve. The piston will therefore move in the direction of the open valve, thereby shifting the associated gear unit. Port b communicates with poppet 'valve 98a. through a groove Hi2, Figs. 9, l0, and channels "12a, 1%, and, similarly to the operation just described, the

opening of poppet'valve 98a when piston64a is in either extreme position, relieves the pressure on one end of the piston, whereupon the pressure on the other end moves the piston until the piston covers the port 98b leading to the open poppet valve.

The spacing of the ports 98b, 9Ib, 92b is such that, accordingly as the one or the other of the area.

. or the other of the poppet valves 90a, 9Ia, 92a.

The piston device 63 is constructed similarly to the'device 64, just described and is similarly movedto three positions, corresponding to the three positions of gears 24, 25, 26, accordingly as cams 81, 88, 89 open poppet valves 81a, 98a, 89a. Since the connection and operation is substantially the same as the device 64 it will not be described in detail.

The piston device 65, Figs. 12, 15 is also similarly controlled for movement to the two positions of the clutch gear 31 by the means of fluid supplied from a channel 910, accordingly as cam 93 opens the one or the other poppet valve 93a, 93a, but in this instance, the piston 660. having only two positions, only two ports are required, as shown at 93b, 93b, Figs, 12, 15.

The various poppet valve cams associated with piston devices 63, 64, 65 are so configurated and positioned that as shaft 34 is rotated the various piston devices and speed change elements are moved to different position combinations resulting in speeds arranged in numerical order, and at points in the rotation of the shaft corresponding to the position of the rotation chart numerals 11 as they are successively readable against indicator '12. This results also in the arrangement of the numerals of the other charts in numerical order, the spacing thereof being determined by the spacing of the numerals on the rotationchart. I I

Means are provided to prevent the shifters from starting to move as the selector shaft 84 is rotated to pass through one or more positions corresponding to undesired speeds. To effect this result and other results latermentioned there is provided a delay, device, generally denoted by the numeral I03, Iflgs. 11, 15. The cam .86, Figs. 8,11, 15 is provided with notches such as 86a, corresponding in number and position to .the speed positions of selector 'shaft 34. The

to locate the cam relative to a poppet valve I06,

the plunger I04 being continuously supplied with fluid from source 69, as by a pipe channel I06, and communicating channels l06a, I060, I060.

The delay device I03 includes a piston plunger I01 and a piston plunger I98 of relatively smaller The left end, Fig. 11, of piston I98 is continuously supplied with fluid through the channels I06, Mia. The right endof piston. I01, Fig.

1, is supplied with fluid from channel I06- through an adjustable needle valve device I09 and a channel mm. The pressure acting on the v right hand end of piston I01 normally forces both scribed, but when the poppet valve I06 is opened by cam 86 during rotation of selector shaft 84 to effect a change in speed, the fluid pressure on piston I 01 is immediately relieved and piston I08 forces piston 101 to the right, to the: position shown in Fig. 11, and'l'n thisp'osition the supply port H is cut off from port III, and port III and channel 91 are connected to a drain channel II4. Piston I01 will almost immediately again move to the left to close the drain and again supply fluid to port III and channel 91, but 'only after needle valve I09 has permitted sufficient fluid to move the piston to flow therethrough. The interval of delay may be varied by adjustment of the needle valve I09, but is sufficient that in rotating shaft 94 at normal adjustment speed no pressure will be available in channel 91 for operation of the piston devices 63, 64, 65 until the selector shaft comes to rest in a desired speed position.

The reverser piston device 41, Figs. 4, 5, 15, 20 may be controlled to shift reverser 6 into the one or the other direction position by the means v of a hand lever II5, Figs. 3, 16, fixed on a sleeve 7 I I6, Figs. 3, 8, which is co-axial-with shafts 16, 84 and coupled with a co-axial sleeve II1, Fig. 8, by the means of a tongue and slot coupling connection II8. Fixed on sleeve II1 is a rotary valvemember II9, Figs. '1, 8 having an annular fluid channel I20, Figs. 8, 14, which is supplied I20 and the different ports I26, I21, Fig. '1, re-

spectively as the lever H5 is moved in opposite directions. The ports I26, I21 respectively communicate through pipe channels I26a, I21a, Figs. 5, '1 with the ports 61, 38, Figs. 4, 20, of reverser piston device 41. Simultaneously with movement of lever Hi to bring either port I26, I21,

' Fig. '1, into communication with the supply channel, the other port is connected to a drain, there being drilled holes I28, I29, Figs. 7, 14, suitably spaced for the purpose and communicating with an interior chamber or annular groove I30 which is extended to the end of the sleeve valve II9 to drain into the interior of the headstock. When hand lever II 6 is in central position both the ports I26, I21 are connected to the drain groove I30, there being a plurality of drilled channels such as the channel I32, Fig. 14, for port I26, suitably positioned in the valve sleeve II9 to effect such connection, a similar channel being provided for the port I21.

By reason of the construction of the sleeve, valve H9 and the construction of the reverser piston device 41, previously described, it will be apparent that the: movement of lever H6 in either direction effects corresponding engagement of the reverser 6, while a central position of the lever II6 effects an intermediate disengaged position of the reverser. v

' Meansare providedto control the reverser 6 from the speed selector device, and which are effective to shift the reverser to a position interrupting the transmission to spindle 3 each time a speed change is eflected, and to return the reverser to its previous position, as determined by lever H5, upon completion of the speed change.

As previously stated the supply of fluidv to eifect movement of the reverseris through the port I2I, Fig. 11, of delay device I03. Port I2I normally receives fluid from supply port I I0,- but in the operation of the device during speed change as previously described port I2I, as well as port either active port 66 or 61 of reverser piston device 4], Figs. 4, to the drain, and since the pert 58 bf"the"reverser piston device is contlnunlessthe connection controlled by lever II5.

has been changed during the speed change operation.

' The brake 42, Figs. 6, 15, is' controlled to be operative from the speed selector device during speed change and tube forced to braking. position whenever lever -I I5 is in the position disemgaging'reverser clutch 6, as follows: Fluid pressure is continuously supplied to the brake piston BIc, Fig. 7, in a direction tourge the brake to braking position, the fluid supply being derived from pump 69 through port I06, Fig. 11, through the channels I06a,. I06b, I06c, pipe connection I33, Figs. '7, 11, and a drilled channel .I34,"Fig. 7. The braking pressure thus applied may "be overcome, whereby to release the brake,

by the c'o'mbined pressure of spring 45, Figs. 6, 15,' and fluid pressure applied to the other side of piston 6Ia, at the-left end, Fig. 7. vthe 'latter'purpose is supplied from port IIIof Fluid for thedela'y device I03,'Fig. 11, through the channel"9'i, Figs.'11, 13, a channel I35, an annular channel I36 in valve sleeve IIO, Figs. '7, 13, and the oneor'the other of the channel grooves I31, 138;"respectively positioned in the valve sleeve I I9" for communicaiton with achannel I39 in the "different clutch engaged positions of lever H5 and sleeve 1 I9. From channel I39 the pressure fluid reaches piston 6Ia through channels I40,

' 'I4I'; Inthe disengaged or central position of reverser control lever II5 the valve sleeve II 9 is in position,'as shown in Fig. 13, to close the channel I39 against. both the supply channels I31, I38, and to-open the channel I39 to the drain I30 through a channel I39a in valve sleeve 9 whereby to cause engagement of the brake. -Thus,'whene ver the reverser 6 is engaged in either direction position the. brake 42 is normally disengaged, but-upon shifting of the reverser to Also, since the supply of brake disengaging fluid is through the port III of delay device. I03, it will -'result that in each operation of speed changin the brake release supply will be connected to drain port II4, Fig. '11, and the brake will then be engaged temporarily irrespective of the position of -the reverser control devices, substantially simultaneously with disengagement of the reverser as previously described. But, as later explained, the brake'is disengagedagain before the reverser is re-engaged; ,zA fluid operated detent member I33a, Fig. 7, is continuously pressed by fluid from the 'pipe channel I33 to engagesuitable notches such as I33b in the sleeve valve .I I9, whereby to define the three positions of the sleeve valve.

By reason of the relative positions of the port III, Fig. 11, which supplies pressure fluid to the shifter devices 63, 64, andalso forreleasing brake 42, and port I2I, which supplies fluid to engage reverser 6, the port I2I is opened to the drain'I I4, during right hand movement of piston I01, before the port III. Therefore, during any speed change operation the reverser 6 is disengaged engaged.

Following connection of port III, Fig. 11, to

- the drain II4 during the right hand shifting of piston I0I the brake 42 is immediately engaged, thereby stopping rotation of spindle 3. Following operation of needle valve I09 to again connect port III tothesupp y part III! the brake 42 is released immediately and before the operation of any of the piston devices 63, 64, 65, there being restricting means operative on each of the piston devices but not on brake releasing means, as follows: Referring to Fig. 15 it will be seen that the I03 reaches the shifter piston devices 03, 64, 65 only through devices I42, I42a, I42b. These devices are serially arranged for the piston device 63 to receive fluid only through device I42, while piston device 64 receives fluid through both devices I42, 142a, and piston device 65 receives fluid through all three devices I42, I420, I421 The several devices I42, I420, I42b .are.s imilar in construction and operation'and therefore onl'ythe device I42a is shown in detail. Referring to Figs. 17, 18 the device includes a spring member I43 .which is flxed by means of screws such as I44 in the channel or supply groove 91!) through which fluid reaches the piston devices 64 and 65, the

. edges of the spring being closely but movably fitted to the sides of the channel groove, and the spring being of such form as to close the channel except as itis sprung by the pressure of the fluid. The springs of each device I42, I42a, I42b are of material resistance, as for instance 15 or 20 pounds. As will be seen from Fig. 15, the devices .63. 64. 65 will therefore operate in sequence as released during any rate change prior to the operation of either piston device 63, 64, 65.

The fluid for the supply ofthe reverser piston device 41 is derived through the-channel I2I of the delay device I03, Fig. 11, as previously explained. The relative positions of ports III'and I2I is such that, following a rate change operation, the left hand movement of piston I01 will connect port III to the supply port IIO prior'to the connection of port I2I for re-engagement of the reverser 6.. Brake 42 will, therefore be released prior to the re-engagement of reverser 6. To'further control the reverser engagement, an engagement control device is provided, generaliy denoted by the numeral I45, Figs. 15, 19.

This device is connected serially in the line leading to the reverser piston device 41 from channel I2I of the delay-device I03, as indicated in Fig. 15, and therefore controls the operation of the reverser under all conditions whether operated from lever I I6 or from therate selector since, as previously. explained, all the fluid for shifting the reverser. is derived from the port I2I.

Device I45 includes a cylinder member I46, Figs. 8, 15, 19,, fixed on .the bottom of the housing member. for the piston devices 63, 64, 65 and adjacent to the delay device I03. A piston I", Fig. 19, provides an enlarged portion I4Ia and a relaso mewhat before the brake 42 is fluid pressure from'port III of the delay device tively smaller portion I 41b, the latter operating 15 in a sleeve I43 fixed in the cylinder bore. The intermediate portion of the piston I41 is exposed to a drain port I49. The smaller area I411) is exposed to the pressure derived from the port I2I and channel I22, Fig. 11 of delay device. I03, through a port I50. exposed through a port I5I and the channel 1220, Figs. 14, 19 to the pressure in the channel I23, Fig. 14 which supplies the reverser piston device 41 through the rotary control valve II9. A passage I52, Fig. 19, continuously communicates with the port I5I and channel I220 at the one end, and at the other end provides a port I53 which is alternatively covered or uncovered by the small piston, end I41b as piston I41 moves to right or left respectively, but even when the piston I41 is to the right some communication exists between the channels I22 and I220, the small piston end,

I41b being ,of slightly reduced diameter at I410 to provide a leakage path past the piston. A port I54 continuously communicates with channel I22- previously described, as a first step in the operation of rate change, the clutch engaging pressure being drained from the supply channel I220 through the one-way valve I55, Fig. 19, port I50, channel I22, and port I2I and drain port Ill of delay device I03, Fig. 11.

v The piston I41 of control device I normally stands to the right in Fig. 19, being forced to this position by the relatively large area exposed at the left piston end. When the fluid is drained from channels I22, I220, during rate change, the piston I41 temporarily remains to the right. But as fluid pressure is restored tochannel I22, following a rate change, the piston I01 immediately moves to the left, because there is then no pressure on the larger left end. Such initial movement of the piston builds up aninitialpressure in the port I5I and channel I220, but the initial pressure is less than thepressure in channel I22 in the same proportion as the area of end 1b is less than the area of end I410. The initial pressure for operation of reverser piston device 41 and the reverser 3 is thereforerelatively low. The

pressure in channel I220 is, however; gradually increased, by leakage through the restricted passage provided by the reduced piston diameterat I41c, until it becomes equal to the pressure-in channel I22 and the reverser clutch plates are then exposed to the full operating pressure.

At some intermediate point in the increase of pressure just described, where the pressure on the larger end I410 of piston I41, Fig. 19, over-balances the pressure on the smaller end I411), the piston I41 again moves to the right to take up its normal operating position. This right hand movement also operates to slow down the equalization of pressures in channels I22, I220 because the right hand movement increases the length of the restricted passageway at I410 and therefore reduces the rate of flow of the pressure equalizing fluid.

For regulation of the period required to build up the pressure in channel I220, Fig.19, there is The larger area 10 is provided a screw I56 which is adjustable to control the position of an abutmentpisto'n I51. The piston I51 is forced against screw I by fluid pressure, and provides an abutment ,determining the extent of the right hand movement of piston I41. The farther piston I41 stands to the right, Fig. 19, following movement to the right during the equalization of pressure between passages I22, I220, the longer the equalizing operation will require.

pressure, thus starting the gearsslowly under partial power to assist engagement thereof during a rate change operation and, in any engagement or reversal, operating to avoid sho'ck-by gradually overcoming the inertia of the driven train.

The sequence of operations involved in a rate change operation is as follows: Assuming that the lever II5, Fig. 16, is in a position to engage reverser 5, and that the desired new spindle speed is for the same direction of spindle rotation. In

such case the only manual operation required is to rotate the selector in either direction by manipulation of the handles 33 of selector 1I until the desired new spindle speed, as listed on chart 13, is in registry with the indicator 12. During such rotation the poppet valve I05 of the delay device I03, Fig. 11, will be opened each time the cam 36 passes through a position intermediate the notches 860, and as soon as the poppet valve is first opened the piston I01 starts to move to the right, Fig. 11, thereby connecting port I2I to drain Ill whereby to efiect a shift of reverser piston device 41 and reverser 3 to intermediate motion interrupting position. Slightly later in the right hand movement of piston I01 of device I03 the port III is alsoopened to the drain Ill, thereby immediately effecting a braking position of brake 42 to stop spindle 3. Upon the selector chart arriving at the desired speed position the poppet valve I05 of device I03 remains closed and fluid flows through needle'valve I09, Fig. 11', to shift piston I01 to its normal left hand position. During such left hand shift it first occurs that port III is opened to pressurefluid, whereupon the spindle brake 42- is immediately released,.and

as the pressure rises in port III the rate change I shifterpiston devices 63, 84, are subjected to pressure in theorder mentioned,- the sequence being controlled by the devices I42, 20,1420

The new speed pomtion of the selector device 1I-eflects a new pomtioncombination of the poppet valve cams and poppet valves associated with the piston devices 33, 64, i5, and therefore the rise ofpressure in these devices will urge the pistons to effect a corresponding new position combination, butonly those pistons will be moved where a poppet valve closed in the previous speed position has been opened in thenew speed position.

.during the rate change operation the result is to engage reverser 6 to effect the same spindle direction as before the rate change, but by reason of the operation of the device I45 to initially restrict the fluid pressure to relatively low value, as

previously explained, the reverser engagement is I event the gears will 'start to turn as soon as the reverser starts to engage, and during the interval while device I45 is efiecting the building up'of the reverser pressure the gears will rotate slowly to insure meshing of the engaging gears.

The construction and control of the reverserinterrupter 6 is such that the device acts as an overload or power limiting device for the machine. To effect this result the friction plate groups [3, l4, Fig. 20, of the different driving clutches are of such friction area and diameter, relative to the effective diameter of piston 48 of the piston device 41, and to" the fluid pressure per unit of piston area, as determined by the relief valve 69b,

Fig. 15, that when an excess of resistance to'theoperation of the transmission is encountered theby the devices M2, 2a, M21), Fig. 15. These devices are serially arranged and each sets up a resistance, and the fluid pressure must be suflicient to overcome the devices while still remaining sufiiciently large to operate the last shifter of theseries. Various other of the control devices also must be considered in determining the construction and control of the interrupter-reverser 6, and particularly the range of fluid pressure necessary for the proper operation of the device I45, Fig. 15, which controls the delayed application of pressure to the interrupter-reverser 6, and the period of gradual increase of pressure.

What is'claimed is:

1. In a transmission and control mechanism the combination of a clutch device including engageable friction members, a. fluid operable piston device, a mechanical train connecting said piston device for pressure engagement of said members at a pressure proportioned to the pressure,

appliedto said device, a fluid pressure source, and

channel means connectirm said source for application of pressure to said device including valve means operable for piston movement in a direction to engage said members, said train including relatively rotatable members operative for said piston device to remain non-rotatable during rotation of the members.

2. In a transmission and control mechanism the combination of ,a clutch device including engageable friction members, a fluid operable piston device, a mechanical train connecting said piston device for pressure engagement of said members at a pressure proportioned to the pressure applied to said device, a fluid pressure source,

and channel means connecting said source for application of pressure to said device including valve means operable for piston movement in a.

direction to engage said members, said train including relatively rotatable coupling members and an anti-friction bearing interposed therebetween for the transmission of pressure axially of the rotatable coupling member in the direction to engage said friction members.

3. In a transmission and control mechanism the combination of a clutch device including engageable friction members, a fluid operable piston device, a mechanical train connecting said piston device for pressure engagement of said members at a pressure proportional to the pressure applied to said device, a fluid pressure source, channel means connectible between said source and device including a controller valve alternatively adjustable to eiIect or to interrupt the channel connection, andmeans operative following the valve adjustment efiecting said connection to effeet a period of increasing pressure on said device.

4. In a transmission'and control mechanism the combination of a. clutch device including engageable friction members, a fluid operable piston device, a mechanical train connecting said piston device for pressure engagement of said members at a pressure proportional to the pressure applied to said device, a fluid pressure source, channel means connectible between said source and device including a controller valve alternatively adjustable to eiiect or to interrupt the channel connection, means for limiting the fluid pressure appliedto said piston device for engaging said clutch members, and means operative following the valve adjustment efiecting the source and device connection to effect a period of increasing pressure on said device.

5. In a transmission and control mechanism the combination of a clutch device including engageable friction members, a fluid operable piston device, a mechanical train connecting said piston device for pressure engagement of said members at a pressure proportional to the pressure applied to said device, afluid pressure source, channel means connectible between said source and device including a controller valve alternatively adjustable to eifect or to interrupt the channel connection, means operative following the valve adjustment efiecting said connection to effect a period of increasing pressure on said device, and meansadjustable for changing the duration of said period of increasing pressure.

6. In a transmission and control mechanism the combination of a rate changer including elements shiftable to various position combinations respectively for difierent rates, driving means for said rate changer including a clutch device comprising engageable friction members, a rate selector adjustable to various positions respectively corresponding to different 'of said position combinations, means operable in accordance with selector adjustment from one to another of its positions for shifting said shiftable elements to a corresponding position combination, a fluid op- ..erable piston device, a mechanical train connecting said piston device for pressure engagement of said clutch members, a pressure fluid source, channel means connectible between said engaging direction thereof a pressure proportional to the fluid pressure applied to said piston device.

7. In artransmission and control mechanism the combination of a rate changer including elements shiftable to various position combinations respectively for different rates, driving means for. said rate changer including a clutch device comprising engageable friction members, a rate seiector adjustable to various positions respectively corresponding to different of said position combinations, means operable in accordance with selector adjustment from one to another of its positions for shifting said shiftable element to a corresponding position combination, a fluid operable piston device,'a mechanical train connecting said piston device for engagement of said clutch members at a mutual pressure proportional to the pressure on said piston device. a, pressure fluid source, channel means connectible between said source and piston device, means operative to establisha predetermined pressure on said piston device from said channel means to engage said clutch members, and means operative upon adjustment of said rate selector to tempressure. 7

8. In a transmission and control mechanism the combination of a reverser clutch device including a plurality of sets of friction members alternatively engageable for different direction efiects, a reversibly fluid operable piston device, a mechanical train connecting said piston device for said alternative engagement of the different sets of friction members and at a pressure proportional to the piston pressure in either engage ment, a fluid pressure source, channel means connecting said fluid source for operation of said piston device including reverser valve means for changing the direction of movementthereof, and means limiting the pressure on said piston device from said source to predetermined value in either direction of piston device movement.

9. In a transmission and control mechanism the combination of a reverser clutchdevice including a plurality of sets of friction members alternatively engageable for different direction effects, a reversibly fluid operable piston'device, a mechanical train connecting said piston device for said alternative engagement'of the different sets of friction members and at a pressure proportional to the piston pressure in either engagement, a fluid pressure source, channel means connecting said fluid source for operation of said piston device including reverser valve means for changing the direction of movement thereof, means limiting the pressure on said piston device from said source to predetermined value in either direction of piston device movement, and means operative following reverser valve adjustment for engagement of either set of friction members to effect a period of pressure-on said piston device materially less than said predetermined pressure.

the combination of a reverser clutch device including a plurality of sets of friction members alternatively engageable for diiierent direction effects, a reversibly fluid operable piston device, a mechanical train connecting said piston device for said alternative engagerhentof the different sets of friction members and at a pressure proportional to the piston pressure in either engagement, a fluid pressure source, channel means ferent direction efl'ect, a rate controller adjustporarily materially reduce said predetermined direction of movement thereof, means limiting 10. In a transmission andcontrol mechanism respectively for different rates, driving means piston device materially less than said predem I termined pressure, and means adjustable for changing the duration of said period.

'11. In a transmission and control mechanism the combination of a rate changer including elements shiftable to various position combina- 15 tions respectively for different rates, driving means for said rate changer including a reverser clutch device providing a plurality of sets of friction members alternatively engageable for difable to various positions respectively correspond- 2o ing to .diiierent of said-position combinations, a

reversibly fluid operable piston device, a mechanthe pressure on said piston device from said .source in either direction-of movement thereof,

and means operative upon adjustment of said rate controller to eifect'a period of pressure on said'piston device materially less than said predetermined pressure.-

12 ha transmission and control mechanism the combination of a rate changer including elements shiftable to various position combinations respectively for different rates, driving means for said rate changer including a reverser clutch device comprising a plurality of sets of friction members alternatively engageable for different direction effect, a rate controller adjustable to various positions respectively corresponding to different of said position combinations, a reversibly fluid operable piston device, a mechanical train connecting said piston device for said alternative engagement of the different sets of friction members and at a. pressure proportioned to the piston pressure in either engagement, a pressure: fluid source, channel means connectible between said source and piston device for either direction of movement thereof, means limiting the pressure on said 'piston device from said source in either direction of movement thereof, means operative upon adjustment of said rate controller to effect a period of pressure on said piston device materially less than said predetermined pressure, and means adjustable for changing the duration of said period.

,13. Ina transmission and control mechanism the combination of a rate changer including elements shiftable to various position combinations engagement of the diiferent sets of friction mem bers and at a pressure proportioned to the piston period of pressure/on said piston device materialpressure in either engagement, a pressure fluid 1y less than said predetermined pressure and source, channel means connectible between saidsubsequently to eflect said predetermined p'ressource and piston device for either direction of. sure.

5 movement thereof, and means operative upon ad- GLENN C. HOLMES. 5 justment of said rate controller to first cited; a 

